HIGH-PRESSURE PRESS

Abstract: A high-pressure press with a high-pressure chamber (1), which at one end has an end member (22, 23, 24) serving as a packing holder, said end member having a support surface (26) which, at maximum pressure in the high-pressure chamber, faces, at a small distance (S), an opposite end surface (25) on the low-pressure cylinder (11) of the press.

Description: Hiσh-nressure press The present invention relates to a high-pressure press comprising a first cylinder element, at least one second cylinder element pressed into the first cylinder element, and a pair of end elements which together with the second cylin¬ der element delimit a high-pressure chamber and of which one end element exhibits a cylinder bore, opening out into the high-pressure chamber, for a high-pressure piston and has parts which are movable to a limited extent in the axial direction and are adapted to form supports for the second cylinder element and a sealing device inserted between the second cylinder element and the high-pressure piston, the axially movable parts being loaded by hydraulic pressure in a direction towards the second cylinder element and the sealing device. High-pressure presses dimensioned for a pressure of up to 14,000 bar in the high-pressure chamber comprise, in a known embodiment, a thick-walled main cylinder of high-tensile steel, which is prestressed by means of several layers of prestressed steel wire wound around the cylinder, and a liner, which may be divided into an outer liner and an inner liner, pressed into the cylinder, in presses operating with such high pressures, very great demands are placed on the quality of the steel wall in the inner liner. The liner must be made with a view to preventing cracks in the inner wall surface. However, it is impossible to avoid that cracks pass which are so small that they cannot be detected with conventional crack detecting methods, but which in the long run, under the influence of the pressure variations during a number of work cycles, unavoidably extend to such an extent that the liner is finally split open and breaks into two parts. When a pressure of the order of magnitude of 14,000 bar is allowed to act against the surfaces of fracture of the liner parts, the parts are subjected to enormous forces when, in principle, they are transformed into annular pistons. The force on one liner part can be taken up directly by the end member fixed against the liner by the press frame. As far as the other part is concerned, however, the conditions are different. In a known embodiment, the second end member, which serves as sealing or packing holder, is connected to a number of piston elements which are provided in evenly distributed axial cylinder bores in the low-pressure piston which generates the press force of the high-pressure piston. In the cylinder bores a cylinder pressure prevails, under the influence of which the packing holder end member balances the pressure on the packing exerted by the pressure in the high- pressure chamber. Since this end member also forms a support for one end of the liner, the liner fracture results in the force on the end member suddenly being multiplied. This force is transmitted via the piston elements to the low-pressure piston. The result is that heavy equipment, up to the order of magnitude of 5 tons, is moved approximately half a metre in one-thousandth of a second, which creates a powerful pressure shock in the whole hydraulic system and leads to the whole press being moved, whereby anchor bolts and connected hydraulic lines are torn off. To avoid the dramatic consequences and the heavy costs which are connected with a liner fracture, the inner liner is regularly changed in good time before the expiry of the expected service life. Such preventive liner exchanges are costly and still do not completely solve the problems of liner fracture, since it has proved that about 10 % of the liners are subjected to fracture within the expected safety margin as regards the number of work cycles. The object of the present invention is to provide a high- pressure press of the kind stated in the introductory part of the description, which is so designed that the above- mentioned problems and costs which are connected with liner fractures can be eliminated and reduced, respectively. This is achieved according to the invention in that the above-mentioned axially movable parts comprise an element with a support surface which is so adapted to a support surface on a stationary element that forces acting in a direction from the high-pressure chamber on the axially movable parts are transmitted to the stationary element when the support surface on the movable element is brought into contact with the support surface on the stationary element. By transferring the force from the liner out to a stationary part in the case of liner fracture, according to the inven¬ tion, which part is suitably an end member on the low- pressure cylinder of the press, instead of taking up the force by means of hydraulic shock absorbers in the low- pressure piston, according to the known method described above, a long movement path of heavy parts and strong pressure shocks in the hydraulic system can be avoided. The movement path of the movable end part need not, in principle, be longer than the maximum extension of the press, which, in practice, entails a movement path amounting to a maximum of 20 mm. In this context it has proved that damage to the press and to equipment connected thereto, such as anchoring devices and hydraulic lines, can be eliminated completely in case of a liner fracture. The invention will be described in greater detail with reference to the embodiments shown in the accompanying drawings, wherein Figure 1 schematically shows a longitudinal section through a known high-pressure press, and Figures 2 and 3, respectively, show corresponding longitudi- nal sections through an embodiment of a press according to the invention, Figure 2 showing an intact press and Figure 3 showing a press after a fracture has occurred on an inner liner. Figure 1 shows a known high-pressure press, which has a high- pressure chamber 1 which is formed from an outer cylinder 2, a surrounding casing 3 of prestressed steel wire, an inner liner 4 pressed into the cylinder, an upper end member 5, and a lower end member 6 which serves as a packing holder for a packing 7. The end member 6 is formed with a cylinder bore 8 for a high-pressure piston 9, which is made integral with a low-pressure piston 10 in a low-pressure cylinder 11. The piston 10 exhibits a plurality of evenly distributed cylinder bores 12, in which piston elements 13 connected to the end member 6 are provided. The force from a cylinder liner part is transmitted, in case of a liner fracture, to the low- pressure-piston 10 via the piston elements 13, which results in the low-pressure piston 10 reversing a distance of about half a metre in a fraction of a second with the consequences described above. Figures 2 and 3 show a high-pressure press according to the invention. In the same way as the prior art press described above, it has a high-pressure chamber 1, which is formed from an outer cylinder 2, a surrounding casing 3 of prestressed steel wire, a liner pressed into the cylinder and divided into an outer liner 4a and an inner liner 4b, an upper end member 5 and a lower end member generally designated 20, which serves as a packing holder for a packing 7. The end member 20 is formed with a cylinder bore 8 for a high- pressure piston 9, which is formed integral with a low- pressure piston 10 in a low-pressure cylinder 11 with a casing 21 of several turns of prestressed steel wire. in the embodiment shown, the end member consists of a piston element 22 movably journalled in the low-pressure cylinder 11, a cylindrical wall element 23 which makes contact with the piston element 22 and has a larger diameter than the piston element 22, and a retaining ring 24, with which the packing 7 and the outer and inner liners 4a and 4b, respectively, make contact, but the piston and wall elements 22, 23 can also be formed integral with each other. In a known manner, the low-pressure cylinder 11 is fixed in a press frame, resting on a press foundation and not further shown, and thus constitutes a stationary part of the press. That end surface 25 of the cylinder 11 which faces the end member 20 is formed as a stop or support surface for an opposite surface 26 on the wall element 23 of the end member. The maximum operating temperature in the high-pressure chamber 1, for example 14,000 bar, is attained at a pressure in the chamber 27 of the low-pressure cylinder 11 which amounts to about 10 % of the pressure in the high-pressure chamber, that is, about 1400 bar in the example described. In the chamber 28 of the low-pressure cylinder, on the side of the end member, a pressure is maintained which is approxi¬ mately 25 % of the pressure in the chamber 27, that is, about 350 bar, by means of a pressure-regulating valve 29. Figure 2 shows the press in intact form with a maximum pressure in the pressure chamber 1. The support surface 26 of the wall element 23 is here located at a distance "S" from the end surface 25 of the cylinder 11. In practice, this distance does not exceed 20 mm and corresponds to the elongation to which the press is subjected when the pressure in the high- pressure chamber rises from a minimum to a maximum. If the inner liner 4b were to burst because of cracking, as illustrated in Figure 3, the pressure in the pressure chamber 1 would act against the fractured surfaces of the liner parts, in which case the liner parts would be exposed to very great oppositely directed forces. The force from the upper part of the liner 4b is taken over by the upper end member 5, which is fixed by the press frame, whereas the force from the lower part of the liner 4b is transmitted to the end member 20 which is then pressed downwards until the support surface 26 of the wall element 23 hits the support surface 25 on the cylinder. In this way, the force is transferred out into the low-pressure cylinder 11 and further out into the press frame after a very short movement of the end member 20, as illu¬ strated by the arrows. It has proved that damage to the press and the associated equipment in case of a liner fracture can be completely eliminated in this way, which in turn means that a liner exchange for preventive purposes does not have to be carried out. The press can quite simply be utilized up to the point where a liner fracture occurs. This permits considerable savings to be made. Among further advantages which can be obtained by using a press according to the invention, as compared with the described prior art press, may be mentioned a shortening of the press by about 2 metres and a simplifica¬ tion of the hydraulics, since hydraulic fluid with a high pressure need not be supplied to any movable parts (cf. the cylinder bores in the low-pressure cylinder of the prior art press) .

Claims: CLAIMS 1. A high-pressure press, comprising a first cylinder element, at least one second cylinder element pressed into the first cylinder element, and a pair of end elements which together with the second cylinder element delimit a high- pressure chamber and of which one end element exhibits a cylinder bore, opening out into the high-pressure chamber, for a high-pressure piston and has parts which are movable to a limited extent in the axial direction and are adapted to form supports for the second cylinder element and a sealing device inserted between the second cylinder element and the high-pressure piston, the axially movable parts being loaded by hydraulic pressure in a direction towards the second cylinder element and the sealing device, characterized in that said axially movable parts (22, 23, 24) comprise an element (23) with a support surface (26) which is so adapted to a support surface (25) on a stationary element (11) that forces acting in a direction from the high-pressure chamber (1) on the axially movable parts are transmitted to the stationary element when the support surface on the movable element makes contact with the support surface on the stationary element. 2. A high-pressure press according to claim 1, characterized in that said axially movable parts (22, 23, 24) comprise a piston element (22) which is axially displace- able in a low-pressure cylinder (11) which forms said statio¬ nary element. 3. A high-pressure press according to claim 2, characterized in that a low-pressure piston (10) journalled in the low-pressure cylinder (11) is connected to the high- pressure piston (9) and that pressure-regulating members (29) are adapted to maintain a pressure in a cylinder space (28) , formed between said piston element and the low-pressure piston, which is lower than the pressure in a cylinder space (27) located on the opposite side of the low-pressure piston. 4. A high-pressure press according to claim 2 or 3, characterized in that the piston element (22) makes contact with an end element (23) which has a surface (26) located opposite to an end surface (25) of the low-pressure cylinder (11) , which end surface faces the high-pressure chamber (1) , said surfaces forming the support surfaces. 5. A high-pressure press according to claim 2 or 3, characterized in that the piston element is formed integral with an end element which has a surface located opposite to an end surface of the low-pressure cylinder, which end sur- face faces the high-pressure chamber, said surfaces forming the support surfaces. 6. A high-pressure press according to any of claims 1-5, characterized in that the support surface (26) on the axially movable element (23) and the support surface (25) on the stationary element (11) are so adapted to each other that, at maximum pressure in the high-pressure chamber (1), they lie at a distance (S) from each other which is at least substantially equal to the elongation of the press at this pressure.

Inventors: BERGMAN CARL, BERGMAN, CARL
Applicants: ASEA BROWN BOVERI, BERGMAN CARL, ASEA BROWN BOVERI AB, BERGMAN, CARL
Application year: 1994
Main classification: B01J3
IPC codes: B21J9, B30B1, B30B11